EP1779008B1 - Sealing arrangement - Google Patents

Sealing arrangement Download PDF

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Publication number
EP1779008B1
EP1779008B1 EP05778423A EP05778423A EP1779008B1 EP 1779008 B1 EP1779008 B1 EP 1779008B1 EP 05778423 A EP05778423 A EP 05778423A EP 05778423 A EP05778423 A EP 05778423A EP 1779008 B1 EP1779008 B1 EP 1779008B1
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EP
European Patent Office
Prior art keywords
sealing arrangement
arrangement according
seal
bristle carrier
carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
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EP05778423A
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German (de)
French (fr)
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EP1779008A1 (en
Inventor
Wilhelm GRÄBELDINGER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MTU Aero Engines AG
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MTU Aero Engines GmbH
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Publication of EP1779008A1 publication Critical patent/EP1779008A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
    • F16J15/3288—Filamentary structures, e.g. brush seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/025—Seal clearance control; Floating assembly; Adaptation means to differential thermal dilatations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/55—Seals
    • F05D2240/56—Brush seals

Definitions

  • the invention relates to a sealing arrangement according to the preamble of patent claim 1. Furthermore, the invention relates to a turbomachine, a gas turbine and a steam turbine.
  • gas turbines include at least one compressor and at least one turbine, with the or each compressor and the or each turbine having a rotor that rotates with respect to a fixed stator.
  • the stator is then, in particular, a stationary housing, to which fixed guide vanes are assigned. Blades are associated with the rotor of a turbine or compressor that rotate with the rotor with respect to the fixed vanes and the fixed housing.
  • a gap between radially inner ends of the stationary vanes and the rotating rotor must be sealed.
  • a seal arrangement for sealing the gap between the radially inner ends of the stationary vanes and the rotating rotor is also referred to as "inner air seal”.
  • Another gap to be sealed is, for example, between the radially outer ends of the rotating blades and the stationary housing.
  • a seal arrangement for sealing the gap between the radially outer ends of the rotating blades and the housing is also referred to as an "outer air seal”.
  • Sealing arrangements between a rotor and a stator are also referred to as dynamic sealing arrangements.
  • the brush seals shows, should here on the DE 195 27 605 C2 or the DE 101 22 732 C2 , respectively US 9,474,305 to get expelled.
  • the brush seal is formed by a plurality of wire-like bristles wound around a bristle carrier, the bristle carrier consisting of a core and a clamping ring.
  • the unit of bristle carrier and bristles, which forms the actual brush seal is arranged in a receiving space which is bounded by a support ring and a cover ring.
  • the bristle carrier is formed from the core and the clamping ring as a closed ring, which is fixedly or immovably positioned in the receiving space, in particular clamped, is. Due to this known in the prior art embodiment of the bristle carrier as a closed ring is the same not elastic, so on the one hand, for example, eccentricities or other mechanical changes of the gap to be sealed between the rotor and stator and on the other hand, for example, different thermal expansion coefficients thermal changes of the sealed gap between rotor and stator of known brush seals can be compensated only limited.
  • the present invention is based on the problem to provide a novel seal assembly.
  • This problem is solved in that the above-mentioned sealing arrangement is further developed by the features of the characterizing part of patent claim 1.
  • the sealing element carrier is formed as a single or multiple interrupted ring, wherein free ends of the sealing element carrier overlap in the region of interruption points in the circumferential direction, wherein contours of the support element and cover element are adapted to the contours of the sealing element carrier and the sealing elements, and wherein at least one end of each part the sealing element carrier is assigned an anti-rotation device.
  • the sealing arrangement according to the invention provides a self-adapting brush seal for sealing a gap between a rotor and a stator, the changes of can be compensated automatically gap without the same here is subject to increased wear.
  • the bristle carrier is no longer formed as a closed ring as in the prior art, but rather as a broken or spiral or open ring, the free ends of which overlap in the circumferential direction.
  • the bristle carrier is freely movable in the receiving space, wherein an anti-rotation device limits the mobility in the circumferential direction.
  • the trained as a spiral ring bristle carrier can on the one hand move eccentrically in the receiving space and on the other hand, the same can adjust by increasing or decreasing its circumference, the inner diameter of the brush seal to an outer diameter of the rotor.
  • the circumferentially overlapping ends of the formed as a spiral ring bristle carrier are offset in the axial direction and in the radial direction, wherein the ends of the bristle carrier are offset such that a radially inner end of the bristle carrier abuts on bristles, which are on the radially outer Fixed end of the bristle carrier.
  • Fig. 1 shows a schematic cross section through a rotor 10 and a rotor 10 surrounding the stator 11 in the axial direction, wherein between the rotor 10 and the stator 11, a gap 12 to be sealed is formed.
  • a brush seal is provided, which is formed from a brush seal housing 13, a bristle carrier 14 and a plurality of bristles 15 fixed to the bristle carrier 14.
  • Fig. 2 shows the arrangement of Figure 1 along the cutting direction II-II in Figure 1 and thus in the circumferential direction.
  • Fig. 3 shows the arrangement of Figs. 1 and 2 along the section line III-III in Fig. 2, and thus in Radialblickraum.
  • the bristle carrier 14 is at least partially positioned in a receiving space 16, wherein free ends of the bristles 15 protrude from the receiving space 16 and stand up to seal the gap 12 on the rotor 10.
  • the receiving space 16 is bounded by a support element 17 and a cover element 18, wherein the support element 17 is arranged on the side of lower pressure of the gap 12 to be sealed.
  • the support member 17 is often referred to as a support ring and the cover member 18 often as a cover ring.
  • the bristle carrier 14 is proposed to form the bristle carrier 14 as a broken or spiral ring, with free ends 19 and 20 of the bristle carrier 14 overlapping in the circumferential direction.
  • the bristle carrier 14 is accordingly designed as an open and elastic ring, which is not fixed in the receiving space 16, but rather is freely movable within certain limits.
  • the bristle carrier 14 is movable in the circumferential direction, wherein the mobility in the circumferential direction in the embodiment shown by two anti-rotation devices 21 and 22 is limited.
  • a first anti-rotation device 21 is associated with a first end 20 of the bristle carrier 14, said first anti-rotation device 21 limits or limits the mobility of the bristle carrier 14 in a main direction of rotation 23 of the rotor 10.
  • the mobility in the circumferential direction is also given a mobility in the radial direction.
  • the inner diameter can automatically adapt to eccentricities or changes in the gap 12. Furthermore, there is to some extent a mobility in the axial direction.
  • the mobilities in the radial direction and in the axial direction are limited by the geometric dimensions of the receiving space 16 or by the contours of the support element 17 or cover element 18.
  • the trained as a spiral ring bristle carrier 14 forms in the embodiment shown both an axial spiral and a diameter spiral.
  • axial spiral is to be understood that the circumferentially overlapping ends 19 and 20 of the bristle carrier 14 are offset from each other in the axial direction.
  • diameter spiral is to be understood that the circumferentially overlapping ends 19 and 20 of the bristle carrier 14 are offset in the radial direction.
  • Fig. 2 on the one hand, the axial offset and the radial offset of the ends 19 and 20 of the bristle carrier 14 are removed.
  • the ends 19 and 20 of the bristle carrier 14 offset from each other such that a radially inner end 19 of the bristle carrier 14 abuts the bristles 15, which are fixed to the radially outer end 20 of the bristle carrier 14.
  • the offset of the free ends 19 and 20 of the bristle carrier 14 in the axial direction would be sufficient, the additional offset thereof in the radial direction to improve the sealing effect is preferred.
  • the bristle carrier 14 is formed as a spiral ring with circumferentially overlapping, free ends 19 and 20, wherein the free ends 19 and 20 are offset from each other at least in the axial direction, preferably also in the radial direction.
  • This spiral or helical contour of the bristle carrier 14 is adapted to the contour of the support member 17 and a support lip 24 thereof.
  • the bearing surface formed by the support element 17 or the support lip 24 for the bristles 15 of the brush seal 13 accordingly follows the helical or helical contour of the brush seal and is formed in a thread-like manner.
  • the bristles 15 of the brush seal 13 are preferably employed with respect to the radial direction. However, the bristles can also run without such a position parallel to the radial direction.
  • the brush seal according to the invention can be used wherever a radial gap between a rotor and a stator is not hermetically sealed.
  • Particularly preferred is the use of the sealing arrangement according to the invention in turbomachines, in particular in gas turbines, such as aircraft engines or in steam turbines.
  • a so-called inner air seal and a so-called Outer Air Seal for sealing a radial gap between the ends of stationary vanes and a rotor or a gap between the free ends of rotating blades and a housing of a compressor or a Turbine of the gas turbine can be realized.
  • the sealing elements may be formed, for example, as strips or lamellae or segments.
  • the strips or lamellae may be laser-cut elements.
  • the segments may overlap one another in the circumferential direction.
  • the strips or lamellae or segments can furthermore also be an integral part of the sealing element carrier.
  • the sealing arrangement according to the invention already provides a minimal leakage of the gap to be sealed in all operating states, whereby the sealing arrangement according to the invention adapts automatically to eccentricities or operational changes in the gap to be sealed.
  • the seal assembly can therefore be referred to as a self-adapting seal. Since the sealing arrangement according to the invention is characterized compared to the sealing arrangements known from the prior art by a significant increase in the permissible overlap to the rotor, there is a significantly wider range of application for brush seals. Furthermore, the wear of the bristles is minimized. Since the inner diameter of the brush seal adapts automatically, it can be manufactured with a larger tolerance, which significantly reduces the manufacturing costs.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Glass Compositions (AREA)
  • Materials For Medical Uses (AREA)
  • Sealing Battery Cases Or Jackets (AREA)

Abstract

A sealing arrangement, especially for a flow engine, for non-hermetically sealing a gap (12) between a rotor (10) and a stator (11), which comprises a seal having a plurality of sealing elements that are fixed to a sealing element support, said sealing element support being at least partially disposed in a receptacle (16) which is defined by a supporting element (17) and a cover element (18) is disclosed. The sealing element support is configured as a ring that is interrupted once or several times. Free ends (19, 20) of the sealing element support overlap in the area of interruptions in the circumferential direction. The contours of the supporting element (17) and the cover element (18) are adapted to the contours of the sealing element support and the sealing elements (15). At least one end (19, 20) of every part of the sealing element support is associated with an antirotation device (21, 22).

Description

Die Erfindung betrifft eine Dichtungsanordnung nach dem Oberbegriff des Patentanspruchs 1. Des Weiteren betrifft die Erfindung eine Strömungsmaschine, eine Gasturbine sowie eine Dampfturbine.The invention relates to a sealing arrangement according to the preamble of patent claim 1. Furthermore, the invention relates to a turbomachine, a gas turbine and a steam turbine.

Bei Strömungsmaschinen, insbesondere bei Gasturbinen wie Flugtriebwerken, gibt es eine Reihe von Anwendungsfällen, in welchen zwei relativ zueinander bewegte Teile, nämlich ein Stator und ein Rotor der Strömungsmaschine, gegen einen die Strömungsmaschine durchlaufenden Gasstrom abzudichten sind. So bestehen insbesondere Gasturbinen unter anderem aus mindestens einem Verdichter sowie mindestens einer Turbine, wobei der oder jeder Verdichter sowie die oder jede Turbine einen Rotor aufweist, der gegenüber einem feststehenden Stator rotiert. Bei dem Stator handelt es sich dann insbesondere um ein feststehendes Gehäuse, dem feststehende Leitschaufeln zugeordnet sind. Dem Rotor einer Turbine bzw. eines Verdichters sind Laufschaufeln zugeordnet, die sich zusammen mit dem Rotor gegenüber den feststehenden Leitschaufeln sowie dem feststehenden Gehäuse drehen.In turbomachines, especially in gas turbines such as aircraft engines, there are a number of applications in which two relatively moving parts, namely a stator and a rotor of the turbomachine, are sealed against a gas stream passing through the flow machine. In particular, gas turbines include at least one compressor and at least one turbine, with the or each compressor and the or each turbine having a rotor that rotates with respect to a fixed stator. The stator is then, in particular, a stationary housing, to which fixed guide vanes are assigned. Blades are associated with the rotor of a turbine or compressor that rotate with the rotor with respect to the fixed vanes and the fixed housing.

Zur Optimierung des Wirkungsgrads von insbesondere Gasturbinen ist es unter anderem erforderlich, Leckageströmungen zwischen dem rotierenden Rotor und dem feststehenden Stator von Verdichter und Turbine zu minimieren. Hierbei muss insbesondere ein Spalt zwischen radial innenliegenden Enden der feststehenden Leitschaufeln und dem sich drehenden Rotor abgedichtet werden. Eine Dichtungsanordnung zur Abdichtung des Spalts zwischen den radial innenliegenden Enden der feststehenden Leitschaufeln und dem sich drehenden Rotor bezeichnet man auch als "inner air seal". Ein weiterer abzudichtender Spalt befindet sich zum Beispiel zwischen den radial außenliegenden Enden der rotierenden Laufschaufeln und dem feststehenden Gehäuse. Eine Dichtungsanordnung zur Abdichtung des Spalts zwischen den radial außenliegenden Enden der rotierenden Laufschaufeln und dem Gehäuse bezeichnet man auch als "outer air seal".Among other things, in order to optimize the efficiency of gas turbines in particular, it is necessary to minimize leakage flows between the rotating rotor and the stationary stator of the compressor and the turbine. In particular, a gap between radially inner ends of the stationary vanes and the rotating rotor must be sealed. A seal arrangement for sealing the gap between the radially inner ends of the stationary vanes and the rotating rotor is also referred to as "inner air seal". Another gap to be sealed is, for example, between the radially outer ends of the rotating blades and the stationary housing. A seal arrangement for sealing the gap between the radially outer ends of the rotating blades and the housing is also referred to as an "outer air seal".

Darüber hinaus sind weitere Spalte zwischen einem rotierenden Rotor und einem feststehenden Stator abzudichten. Dichtungsanordnungen zwischen einem Rotor und einem Stator werden auch als dynamische Dichtungsanordnungen bezeichnet.In addition, further gaps between a rotating rotor and a stationary stator are sealed. Sealing arrangements between a rotor and a stator are also referred to as dynamic sealing arrangements.

Aus dem Stand der Technik ist es bereits bekannt, dynamische Dichtungsanordnungen zur nicht-hermetischen Abdichtung eines Spalts zwischen einem Rotor und einem Stator als Bürstendichtung auszubilden. Als Stand der Technik, der Bürstendichtungen zeigt, soll hier auf die DE 195 27 605 C2 oder die DE 101 22 732 C2 , bzw US 9 474 305 verwiesen werden. Bei den obigen aus dem Stand der Technik bekannten Bürstendichtungen wird die Bürstendichtung von mehreren drahtartigen Borsten gebildet, die um einen Borstenträger gewickelt sind, wobei der Borstenträger aus einem Kern und einem Klemmring besteht. Die Einheit aus Borstenträger und Borsten, welche die eigentliche Bürstendichtung bildet, ist in einem Aufnahmeraum angeordnet, welcher von einem Stützring und einem Deckring begrenzt ist.It is already known from the prior art, dynamic sealing assemblies for non-hermetic sealing of a gap between a Form rotor and a stator as a brush seal. As the state of the art, the brush seals shows, should here on the DE 195 27 605 C2 or the DE 101 22 732 C2 , respectively US 9,474,305 to get expelled. In the above brush seals known from the prior art, the brush seal is formed by a plurality of wire-like bristles wound around a bristle carrier, the bristle carrier consisting of a core and a clamping ring. The unit of bristle carrier and bristles, which forms the actual brush seal is arranged in a receiving space which is bounded by a support ring and a cover ring.

Bei den Bürstendichtungen gemäß DE 195 27 605 C2 sowie DE 101 22 732 C2 ist der Borstenträger aus dem Kern sowie dem Klemmring als geschlossener Ring ausgebildet, der im Aufnahmeraum fest bzw. unbeweglich positioniert, insbesondere geklemmt, ist. Bedingt durch diese nach dem Stand der Technik bekannte Ausgestaltung des Borstenträgers als geschlossener Ring ist derselbe nicht elastisch, sodass einerseits zum Beispiel Exzentrizitäten oder sonstige mechanische Veränderungen des abzudichtenden Spalts zwischen Rotor und Stator und andererseits durch zum Beispiel unterschiedliche thermische Ausdehnungskoeffizienten bedingte thermische Veränderungen des abzudichtenden Spalts zwischen Rotor und Stator von bekannten Bürstendichtungen nur eingeschränkt ausgeglichen werden können. Bei den aus dem Stand der Technik bekannten Bürstendichtungen erfolgt der Ausgleich eines sich verändernden, abzudichtenden Spalts ausschließlich durch das Einfedern der Borsten, wodurch einerseits eine erhebliche Reibungswärme erzeugt wird und wodurch andererseits die Borsten der Bürstendichtung einem deutlichen Verschleiß unterliegen. Die aus dem Stand der Technik bekannten Bürstendichtungen können demnach sich zum Beispiel während des Betriebs einstellende Änderungen des abzudichtenden Spalts nur unzureichend kompensieren.For the brush seals according to DE 195 27 605 C2 such as DE 101 22 732 C2 the bristle carrier is formed from the core and the clamping ring as a closed ring, which is fixedly or immovably positioned in the receiving space, in particular clamped, is. Due to this known in the prior art embodiment of the bristle carrier as a closed ring is the same not elastic, so on the one hand, for example, eccentricities or other mechanical changes of the gap to be sealed between the rotor and stator and on the other hand, for example, different thermal expansion coefficients thermal changes of the sealed gap between rotor and stator of known brush seals can be compensated only limited. In the known from the prior art brush seals the compensation of a changing gap to be sealed takes place exclusively by the compression of the bristles, whereby on the one hand a considerable frictional heat is generated and on the other hand, the bristles of the brush seal subject to significant wear. Accordingly, the brush seals known from the prior art can only insufficiently compensate for changes in the gap to be sealed during operation, for example.

Hiervon ausgehend liegt der vorliegenden Erfindung das Problem zu Grunde, eine neuartige Dichtungsanordnung zu schaffen. Dieses Problem wird dadurch gelöst, dass die eingangs genannte Dichtungsanordnung durch die Merkmale des kennzeichnenden Teils des Patentanspruchs 1 weitergebildet ist. Erfindungsgemäß ist der Dichtelementträger als einfach oder mehrfach unterbrochener Ring ausgebildet, wobei freie Enden des Dichtelementträgers sich im Bereich von Unterbrechungsstellen in Umfangsrichtung überlappen, wobei Konturen des Stützelements und Deckelements an die Konturen des Dichtelementträgers und der Dichtelemente angepasst sind, und wobei mindestens einem Ende jedes Teils des Dichtelementträgers eine Verdrehsicherungseinrichtung zugeordnet ist.On this basis, the present invention is based on the problem to provide a novel seal assembly. This problem is solved in that the above-mentioned sealing arrangement is further developed by the features of the characterizing part of patent claim 1. According to the invention, the sealing element carrier is formed as a single or multiple interrupted ring, wherein free ends of the sealing element carrier overlap in the region of interruption points in the circumferential direction, wherein contours of the support element and cover element are adapted to the contours of the sealing element carrier and the sealing elements, and wherein at least one end of each part the sealing element carrier is assigned an anti-rotation device.

In der bevorzugten Ausführungsform der Erfindung, in welcher die Dichtung als Bürstendichtung, die Dichtelemente als Borsten und der Dichtelementträger als Borstenträger ausgebildet ist/sind, stellt die erfindungsgemäße Dichtungsanordnung eine selbstadaptierende Bürstendichtung zur Abdichtung eines Spalts zwischen einem Rotor und einem Stator bereit, die Änderungen des abzudichtenden Spalts selbsttätig ausgleichen kann, ohne dass dieselbe hierbei einem erhöhten Verschleiß unterliegt. Der Borstenträger ist nicht mehr wie beim Stand der Technik als geschlossener Ring ausgebildet, sondern vielmehr als unterbrochener bzw. spiralförmiger bzw. offener Ring, dessen freie Enden sich in Umfangsrichtung überlappen. Ferner ist der Borstenträger im Aufnahmeraum frei beweglich, wobei eine Verdrehsicherungseinrichtung die Beweglichkeit in Umfangsrichtung begrenzt. Der als spiralförmiger Ring ausgebildete Borstenträger kann sich einerseits im Aufnahmeraum exzentrisch verschieben und andererseits kann derselbe durch Zunahme oder Abnahme seines Umfangs den Innendurchmesser der Bürstendichtung an einen Außendurchmesser des Rotors anpassen.In the preferred embodiment of the invention in which the seal is formed as a brush seal, the sealing elements as bristles and the sealing element carrier as a bristle carrier, the sealing arrangement according to the invention provides a self-adapting brush seal for sealing a gap between a rotor and a stator, the changes of can be compensated automatically gap without the same here is subject to increased wear. The bristle carrier is no longer formed as a closed ring as in the prior art, but rather as a broken or spiral or open ring, the free ends of which overlap in the circumferential direction. Furthermore, the bristle carrier is freely movable in the receiving space, wherein an anti-rotation device limits the mobility in the circumferential direction. The trained as a spiral ring bristle carrier can on the one hand move eccentrically in the receiving space and on the other hand, the same can adjust by increasing or decreasing its circumference, the inner diameter of the brush seal to an outer diameter of the rotor.

Hierdurch ergeben sich eine Vielzahl von Vorteilen der erfindungsgemäßen Dichtungsanordnung. In allen Betriebszuständen kann durch die selbsttätige Anpassung des Innendurchmessers der Bürstendichtung eine minimale Leckage des abzudichtenden Spalts sichergestellt werden. Sowohl Exzentrizitäten des Rotors bzw. Stators als auch im Betrieb bedingte Spaltänderungen können selbsttätig ausgeglichen werden. Hierdurch ergibt sich eine deutliche Erweiterung des Einsatzspektrums von Bürstendichtungen, bei gleichzeitiger Verringerung des Verschleißes derselben.This results in a large number of advantages of the sealing arrangement according to the invention. In all operating states can be ensured by the automatic adjustment of the inner diameter of the brush seal a minimal leakage of the gap to be sealed. Both eccentricities of the rotor or stator and also in operation caused gap changes can be compensated automatically. This results in a significant expansion of the range of use of brush seals, while reducing the wear of the same.

Nach einer vorteilhaften Weiterbildung der Erfindung sind die sich in Umfangsrichtung überlappenden Enden des als spiralförmiger Ring ausgebildeten Borstenträgers in Axialrichtung und in Radialrichtung versetzt, wobei die Enden des Borstenträgers derart versetzt sind, dass ein radial innenliegendes Ende des Borstenträgers an Borsten anliegt, die am radial außenliegenden Ende des Borstenträgers fixiert sind.According to an advantageous embodiment of the invention, the circumferentially overlapping ends of the formed as a spiral ring bristle carrier are offset in the axial direction and in the radial direction, wherein the ends of the bristle carrier are offset such that a radially inner end of the bristle carrier abuts on bristles, which are on the radially outer Fixed end of the bristle carrier.

Bevorzugte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen und der nachfolgenden Beschreibung. Ein Ausführungsbeispiel der Erfindung wird, ohne hierauf beschränkt zu sein, an Hand der Zeichnung näher erläutert. Dabei zeigt:

Fig. 1
einen schematisierten Querschnitt durch einen Rotor und einen Stator zusammen mit einer erfindungsgemäßen Dichtungsanordnung zur nicht-hermetischen Abdichtung eines Spalts zwischen dem Rotor und dem Stator;
Fig. 2
einen Querschnitt durch die erfindungsgemäße Dichtungsanordnung entlang der Schnittlinie II-II gemäß Fig. 1; und
Fig. 3
einen Querschnitt durch die erfindungsgemäße Dichtungsanordnung entlang der Schnittlinie III-III gemäß Fig. 2.
Preferred embodiments of the invention will become apparent from the dependent claims and the description below. An embodiment of the invention will be described, without being limited thereto, with reference to the drawing. Showing:
Fig. 1
a schematic cross section through a rotor and a stator together with a sealing arrangement according to the invention for non-hermetic sealing of a gap between the rotor and the stator;
Fig. 2
a cross section through the seal assembly according to the invention along the section line II-II of FIG. 1; and
Fig. 3
a cross section through the seal assembly according to the invention along the section line III-III of FIG. 2nd

Nachfolgend wird die hier vorliegende Erfindung unter Bezugnahme auf Fig. 1 bis 3 in größerem Detail beschrieben.Hereinafter, the present invention will be described in more detail with reference to FIGS. 1 to 3.

Fig. 1 zeigt einen schematisierten Querschnitt durch einen Rotor 10 sowie einen den Rotor 10 umschließenden Stator 11 in axialer Blickrichtung, wobei zwischen dem Rotor 10 und dem Stator 11 ein abzudichtender Spalt 12 ausgebildet ist. Zur Abdichtung des Spalts 12 zwischen dem Rotor 10 und dem Stator 11 ist eine Bürstendichtung vorgesehen, die aus einem Bürstendichtungsgehäuse 13, einem Borstenträger 14 und mehreren am Borstenträger 14 fixierten Borsten 15 gebildet wird. Fig. 2 zeigt die Anordnung der Fig. 1 entlang der Schnittrichtung II-II in Fig. 1 und damit in Umfangsblickrichtung; Fig. 3 zeigt die Anordnung der Fig. 1 und 2 entlang der Schnittlinie III-III in Fig. 2, und damit in Radialblickrichtung.Fig. 1 shows a schematic cross section through a rotor 10 and a rotor 10 surrounding the stator 11 in the axial direction, wherein between the rotor 10 and the stator 11, a gap 12 to be sealed is formed. For sealing the gap 12 between the rotor 10 and the stator 11, a brush seal is provided, which is formed from a brush seal housing 13, a bristle carrier 14 and a plurality of bristles 15 fixed to the bristle carrier 14. Fig. 2 shows the arrangement of Figure 1 along the cutting direction II-II in Figure 1 and thus in the circumferential direction. Fig. 3 shows the arrangement of Figs. 1 and 2 along the section line III-III in Fig. 2, and thus in Radialblickrichtung.

Wie Fig. 2 entnommen werden kann, ist der Borstenträger 14 zumindest abschnittsweise in einem Aufnahmeraum 16 positioniert, wobei freie Enden der Borsten 15 aus dem Aufnahmeraum 16 herausragen und zur Abdichtung des Spalts 12 auf dem Rotor 10 aufstehen. Der Aufnahmeraum 16 wird von einem Stützelement 17 sowie einem Deckelement 18 begrenzt, wobei das Stützelement 17 auf der Seite niedrigeren Drucks des abzudichtenden Spalts 12 angeordnet ist. Das Stützelement 17 wird häufig auch als Stützring und das Deckelement 18 häufig auch als Deckring bezeichnet.2, the bristle carrier 14 is at least partially positioned in a receiving space 16, wherein free ends of the bristles 15 protrude from the receiving space 16 and stand up to seal the gap 12 on the rotor 10. The receiving space 16 is bounded by a support element 17 and a cover element 18, wherein the support element 17 is arranged on the side of lower pressure of the gap 12 to be sealed. The support member 17 is often referred to as a support ring and the cover member 18 often as a cover ring.

Im Sinne der hier vorliegenden Erfindung wird vorgeschlagen, den Borstenträger 14 als unterbrochenen bzw. spiralförmigen Ring auszubilden, wobei freie Enden 19 und 20 des Borstenträgers 14 sich in Umfangsrichtung überlappen. Der Borstenträger 14 ist demnach als offener und elastischer Ring ausgebildet, der im Aufnahmeraum 16 nicht fixiert ist, sondern vielmehr innerhalb gewisser Grenzen frei beweglich ist.For the purposes of the present invention, it is proposed to form the bristle carrier 14 as a broken or spiral ring, with free ends 19 and 20 of the bristle carrier 14 overlapping in the circumferential direction. The bristle carrier 14 is accordingly designed as an open and elastic ring, which is not fixed in the receiving space 16, but rather is freely movable within certain limits.

So ist der Borstenträger 14 in Umfangsrichtung beweglich, wobei die Beweglichkeit in Umfangsrichtung im gezeigten Ausführungsbeispiel durch zwei Verdrehsicherungseinrichtungen 21 und 22 begrenzt wird. Eine erste Verdrehsicherungseinrichtung 21 ist einem ersten Ende 20 des Borstenträgers 14 zugeordnet, wobei diese erste Verdrehsicherungseinrichtung 21 die Beweglichkeit des Borstenträgers 14 in einer Hauptdrehrichtung 23 des Rotors 10 limitiert bzw. begrenzt. Eine zweite Verdrehsicherungseinrichtung 22, die dem zweiten freien Ende 19 des Borstenträgers 14 zugeordnet ist, begrenzt die Beweglichkeit des Borstenträgers 14 entgegengesetzt zur Hauptdrehrichtung 23 des Rotors 10. Neben der Beweglichkeit in Umfangsrichtung ist weiterhin eine Beweglichkeit in Radialrichtung gegeben. Durch die Beweglichkeit in Radialrichtung kann sich der Innendurchmesser selbsttätig an Exzentrizitäten bzw. Änderungen des Spalts 12 anpassen. Weiterhin ist im gewissen Umfang eine Beweglichkeit in Axialrichtung gegeben. Die Beweglichkeiten in Radialrichtung sowie Axialrichtung werden durch die geometrischen Abmessungen des Aufnahmeraums 16 bzw. durch die Konturen von Stützelement 17 bzw. Deckelement 18 begrenzt.Thus, the bristle carrier 14 is movable in the circumferential direction, wherein the mobility in the circumferential direction in the embodiment shown by two anti-rotation devices 21 and 22 is limited. A first anti-rotation device 21 is associated with a first end 20 of the bristle carrier 14, said first anti-rotation device 21 limits or limits the mobility of the bristle carrier 14 in a main direction of rotation 23 of the rotor 10. A second anti-rotation device 22, which is associated with the second free end 19 of the bristle carrier 14, limits the mobility of the bristle carrier 14 opposite to the main direction of rotation 23 of the rotor 10. In addition to the mobility in the circumferential direction is also given a mobility in the radial direction. Due to the mobility in the radial direction, the inner diameter can automatically adapt to eccentricities or changes in the gap 12. Furthermore, there is to some extent a mobility in the axial direction. The mobilities in the radial direction and in the axial direction are limited by the geometric dimensions of the receiving space 16 or by the contours of the support element 17 or cover element 18.

Der als spiralförmiger Ring ausgebildete Borstenträger 14 bildet im gezeigten Ausführungsbeispiel sowohl eine Axialspirale als auch eine Durchmesserspirale. Unter Axialspirale soll verstanden werden, dass die sich in Umfangsrichtung überlappenden Enden 19 und 20 des Borstenträgers 14 in Axialrichtung zueinander versetzt sind. Unter Durchmesserspirale soll verstanden werden, dass die sich in Umfangsrichtung überlappenden Enden 19 und 20 des Borstenträgers 14 in Radialrichtung versetzt sind. Fig. 2 kann einerseits der axiale Versatz als auch der radiale Versatz der Enden 19 und 20 des Borstenträgers 14 entnommen werden. Dabei sind gemäß Fig. 2 die Enden 19 und 20 des Borstenträgers 14 derart zueinander versetzt, dass ein radial innenliegendes Ende 19 des Borstenträgers 14 an den Borsten 15 anliegt, die am radial außenliegenden Ende 20 des Borstenträgers 14 fixiert sind. Obwohl im Sinne der hier vorliegenden Erfindung der Versatz der freien Enden 19 und 20 des Borstenträgers 14 in Axialrichtung ausreichend wäre, ist der zusätzliche Versatz derselben in Radialrichtung zur Verbesserung der Dichtwirkung bevorzugt.The trained as a spiral ring bristle carrier 14 forms in the embodiment shown both an axial spiral and a diameter spiral. Under axial spiral is to be understood that the circumferentially overlapping ends 19 and 20 of the bristle carrier 14 are offset from each other in the axial direction. Under diameter spiral is to be understood that the circumferentially overlapping ends 19 and 20 of the bristle carrier 14 are offset in the radial direction. Fig. 2, on the one hand, the axial offset and the radial offset of the ends 19 and 20 of the bristle carrier 14 are removed. 2, the ends 19 and 20 of the bristle carrier 14 offset from each other such that a radially inner end 19 of the bristle carrier 14 abuts the bristles 15, which are fixed to the radially outer end 20 of the bristle carrier 14. Although in the sense of the present invention, the offset of the free ends 19 and 20 of the bristle carrier 14 in the axial direction would be sufficient, the additional offset thereof in the radial direction to improve the sealing effect is preferred.

Wie bereits mehrfach erwähnt, ist der Borstenträger 14 als spiralförmiger Ring mit sich in Umfangsrichtung überlappenden, freien Enden 19 und 20 ausgebildet, wobei die freien Enden 19 und 20 zumindest in Axialrichtung, vorzugsweise auch in Radialrichtung, zueinander versetzt sind. Hierdurch ergibt sich eine spiralförmige bzw. schraubenlinienförmige Kontur des Borstenträgers 14, der dann auch die am Borstenträger 14 fixierten Borsten 15 folgen. Dieser spiralförmigen bzw. schraubenlinienförmigen Kontur des Borstenträgers 14 ist die Kontur des Stützelements 17 bzw. einer Stützlippe 24 desselben angepasst. Die durch das Stützelement 17 bzw. die Stützlippe 24 ausgebildete Anlagefläche für die Borsten 15 der Bürstendichtung 13 folgt demnach der spiralförmigen bzw. schraubenlinienförmigen Kontur der Bürstendichtung und ist dabei gewindeartig ausgebildet.As already mentioned several times, the bristle carrier 14 is formed as a spiral ring with circumferentially overlapping, free ends 19 and 20, wherein the free ends 19 and 20 are offset from each other at least in the axial direction, preferably also in the radial direction. This results in a spiral or helical contour of the bristle carrier 14, which then also follow the bristles 15 fixed on the bristle carrier 14. This spiral or helical contour of the bristle carrier 14 is adapted to the contour of the support member 17 and a support lip 24 thereof. The bearing surface formed by the support element 17 or the support lip 24 for the bristles 15 of the brush seal 13 accordingly follows the helical or helical contour of the brush seal and is formed in a thread-like manner.

Wie Fig. 1 zeigt, sind die Borsten 15 der Bürstendichtung 13 gegenüber der Radialrichtung vorzugsweise angestellt. Die Borsten können jedoch auch ohne eine derartige Anstellung parallel zur Radialrichtung verlaufen.As shown in Fig. 1, the bristles 15 of the brush seal 13 are preferably employed with respect to the radial direction. However, the bristles can also run without such a position parallel to the radial direction.

Die erfindungsgemäße Bürstendichtung kann überall dort eingesetzt werden, wo zwischen einem Rotor und einem Stator ein radialer Spalt nichthermetisch abzudichten ist. Besonders bevorzugt ist die Verwendung der erfindungsgemäßen Dichtungsanordnung in Strömungsmaschinen, insbesondere in Gasturbinen, wie Flugtriebwerken oder auch in Dampfturbinen. So kann mit der erfindungsgemäßen Dichtungsanordnung zum Beispiel eine sogenannte Inner Air Seal als auch eine sogenannte Outer Air Seal zur Abdichtung eines Radialspalts zwischen den Enden feststehender Leitschaufeln und einem Rotor bzw. eines Spalts zwischen den freien Enden rotierender Laufschaufeln und einem Gehäuse eines Verdichters bzw. einer Turbine der Gasturbine realisiert werden.The brush seal according to the invention can be used wherever a radial gap between a rotor and a stator is not hermetically sealed. Particularly preferred is the use of the sealing arrangement according to the invention in turbomachines, in particular in gas turbines, such as aircraft engines or in steam turbines. Thus, with the sealing arrangement according to the invention, for example, a so-called inner air seal and a so-called Outer Air Seal for sealing a radial gap between the ends of stationary vanes and a rotor or a gap between the free ends of rotating blades and a housing of a compressor or a Turbine of the gas turbine can be realized.

Die Dichtung muss nicht als Bürstendichtung ausgebildet sein. Vielmehr können im Sinne der hier vorliegenden Erfindung die Dichtelemente zum Beispiel als Streifen oder Lamellen oder Segmente ausgebildet sein. Bei den Streifen oder Lamellen kann es sich um lasergeschnittene Elemente handeln. Die Segmente können in Umfangsrichtung einander überlappen. Die Streifen oder Lamellen oder Segmente können des weiteren auch integraler Bestandteil des Dichtelementträgers sein.The seal does not have to be designed as a brush seal. Rather, in the sense of the present invention, the sealing elements may be formed, for example, as strips or lamellae or segments. The strips or lamellae may be laser-cut elements. The segments may overlap one another in the circumferential direction. The strips or lamellae or segments can furthermore also be an integral part of the sealing element carrier.

Die erfindungsgemäße Dichtungsanordnung stellt in allen Betriebszuständen eine minimale Leckage des abzudichtenden Spalts bereits, wobei sich die erfindungsgemäße Dichtungsanordnung selbsttätig an Exzentrizitäten oder betrieblichbedingte Veränderungen des abzudichtenden Spalts anpasst. Die Dichtungsanordnung kann demnach als selbstadaptierende Dichtung bezeichnet werden. Da die erfindungsgemäße Dichtungsanordnung gegenüber den aus dem Stand der Technik bekannten Dichtungsanordnungen durch eine deutliche Vergrößerung der zulässigen Überdeckung zum Rotor gekennzeichnet ist, ergibt sich ein deutlich erweiterter Einsatzbereich für Bürstendichtungen. Weiterhin wird der Verschleiß der Borsten minimiert. Da sich der Innendurchmesser der Bürstendichtung selbsttätig anpasst, kann dieselbe mit einer größeren Toleranz gefertigt werden, wodurch sich die Herstellkosten deutlich reduzieren.The sealing arrangement according to the invention already provides a minimal leakage of the gap to be sealed in all operating states, whereby the sealing arrangement according to the invention adapts automatically to eccentricities or operational changes in the gap to be sealed. The seal assembly can therefore be referred to as a self-adapting seal. Since the sealing arrangement according to the invention is characterized compared to the sealing arrangements known from the prior art by a significant increase in the permissible overlap to the rotor, there is a significantly wider range of application for brush seals. Furthermore, the wear of the bristles is minimized. Since the inner diameter of the brush seal adapts automatically, it can be manufactured with a larger tolerance, which significantly reduces the manufacturing costs.

Claims (16)

  1. A sealing arrangement, in particular for a flow machine, for the non-hermetic sealing of a gap (12) between a rotor (10) and a stator (11), with a seal provided with a plurality of seal elements that are fixed to a seal element carrier, wherein the seal element carrier is arranged at least in sections in an accommodation space (16), which is bounded by a support element (17) and a cover element (18), characterised in that the seal element carrier is formed as a singly or multiply interrupted ring, wherein free ends (19, 20) of the seal element carrier overlap in the region of interruption sites in the circumferential direction, wherein contours of the support element (17) and cover element (18) are adapted to the contours of the seal element carrier and of the seal elements (15), and wherein a rotation prevention device (21, 22) is associated with at least one end (19, 20) of each part of the seal element carrier.
  2. A sealing arrangement according to claim 1, characterised in that the seal is formed as a brush seal, the seal elements are formed as bristles (15), and the seal element carrier is formed as a bristle carrier (14).
  3. A sealing arrangement according to claim 2, characterised in that the bristle carrier (14) is formed as an open and elastic ring, which is movably mounted in the accommodation space (16).
  4. A sealing arrangement according to claim 3, characterised in that the bristle carrier (14) can move in the circumferential direction, wherein the or each rotation prevention device (20, 21) limits the mobility in the circumferential direction.
  5. A sealing arrangement according to one or more of claims 2 to 4, characterised in that a first rotation prevention device (21) is associated with a first end (20) of the bristle carrier (14), which device limits the mobility in a main rotational direction of the rotor (10).
  6. A sealing arrangement according to claim 5, characterised in that a second rotation prevention device (22) is associated with a second end (19) of the bristle carrier (14), which device limits the mobility in the direction opposite to the main rotational direction.
  7. A sealing arrangement according to one or more of claims 2 to 6, characterised in that the ends (19, 20), overlapping in the circumferential direction, of the bristle carrier (14) formed as a spiral-shaped ring are displaced in the axial direction.
  8. A sealing arrangement according to one or more of claims 2 to 7, characterised in that the ends (19, 20), overlapping in the circumferential direction, of the bristle carrier (14) formed as a spiral-shaped ring are displaced in the axial direction and in the radial direction.
  9. A sealing arrangement according to claim 8, characterised in that the ends (19, 20) of the bristle carrier (14) are displaced in such a way that a radially inner lying end (19) of the bristle carrier (14) rests on bristles (15), which are fixed to the radially outer lying end (20) of the bristle carrier (14).
  10. A sealing arrangement according to one or more of claims 2 to 9, characterised in that the contour of the support element (17) is adapted to the contour of the bristle carrier (14) formed as a spiral-shaped ring in such a way that the contour of the support element (17) follows in a thread-like manner the spiral-shaped or helical-shaped contour of the bristle carrier (14).
  11. A sealing arrangement according to one or more of claims 2 to 10, characterised in that the bristles (15) of the brush seal are arranged parallel to the radial direction and are adjusted with respect to the radial direction.
  12. A sealing arrangement according to claim 1, characterised in that the seal elements are formed as strips, disks, plates or segments.
  13. A sealing arrangement according to one or more of claims 1 to 12, characterised in that the support element and the cover element are formed as contours on the stator.
  14. A flow machine with at least one sealing arrangement according to one or more of claims 1 to 13.
  15. A gas turbine, in particular an aircraft propulsion unit, with at least one sealing arrangement according to one or more of claims 1 to 13.
  16. A steam turbine with at least one sealing arrangement according to one or more of claims 1 to 13.
EP05778423A 2004-08-11 2005-08-03 Sealing arrangement Not-in-force EP1779008B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004038933A DE102004038933A1 (en) 2004-08-11 2004-08-11 sealing arrangement
PCT/DE2005/001366 WO2006015577A1 (en) 2004-08-11 2005-08-03 Sealing arrangement

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EP1779008A1 EP1779008A1 (en) 2007-05-02
EP1779008B1 true EP1779008B1 (en) 2007-12-12

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EP05778423A Not-in-force EP1779008B1 (en) 2004-08-11 2005-08-03 Sealing arrangement

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US (1) US7637719B2 (en)
EP (1) EP1779008B1 (en)
JP (1) JP2008509336A (en)
AT (1) ATE380957T1 (en)
DE (2) DE102004038933A1 (en)
ES (1) ES2296220T3 (en)
WO (1) WO2006015577A1 (en)

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Publication number Publication date
US20070252336A1 (en) 2007-11-01
EP1779008A1 (en) 2007-05-02
JP2008509336A (en) 2008-03-27
ATE380957T1 (en) 2007-12-15
DE102004038933A1 (en) 2006-02-23
DE502005002249D1 (en) 2008-01-24
ES2296220T3 (en) 2008-04-16
US7637719B2 (en) 2009-12-29
WO2006015577A1 (en) 2006-02-16

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